U.S. patent number 7,867,130 [Application Number 12/826,196] was granted by the patent office on 2011-01-11 for multi-speed transmission.
This patent grant is currently assigned to GM Global Technology Operations, Inc.. Invention is credited to Clinton E. Carey, Edwin T. Grochowski, James M. Hart, Andrew W. Phillips, Scott H. Wittkopp, Elizabeth I. Wooden.
United States Patent |
7,867,130 |
Carey , et al. |
January 11, 2011 |
Multi-speed transmission
Abstract
A transmission is provided having an input member, an output
member, four planetary gear sets, a plurality of coupling members
and a plurality of torque transmitting devices. Each of the
planetary gear sets includes a sun gear member, a planet carrier
member, and a ring gear member. The torque transmitting devices
include clutches and brakes arranged within a transmission
housing.
Inventors: |
Carey; Clinton E. (Highland,
MI), Hart; James M. (Belleville, MI), Wittkopp; Scott
H. (Ypsilanti, MI), Phillips; Andrew W. (Rochester,
MI), Grochowski; Edwin T. (Howell, MI), Wooden; Elizabeth
I. (Farmington Hills, MI) |
Assignee: |
GM Global Technology Operations,
Inc. (Detroit, MI)
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Family
ID: |
39719869 |
Appl.
No.: |
12/826,196 |
Filed: |
June 29, 2010 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20100267516 A1 |
Oct 21, 2010 |
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Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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11746396 |
May 9, 2007 |
7775931 |
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Current U.S.
Class: |
475/277;
475/282 |
Current CPC
Class: |
F16H
3/66 (20130101); F16H 2200/2043 (20130101); F16H
2200/2012 (20130101); F16H 2200/006 (20130101) |
Current International
Class: |
F16H
3/62 (20060101) |
Field of
Search: |
;475/275,277,282,288,311,317 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Le; David D
Assistant Examiner: Young; Edwin A.
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATIONS
This patent application is a divisional application of U.S. patent
application Ser. No. 11/746,396, filed May 9, 2007, which, in turn,
claims the benefit of U.S. provisional patent application Ser. No.
60/895,411, filed on Mar. 16, 2007. The disclosure of the above
application is incorporated herein by reference.
Claims
What is claimed is:
1. A transmission comprising: an input member; an output member; a
transmission housing having a first wall, a second wall, and a
third wall extending between the first and second walls; a first,
second, third and fourth planetary gear set disposed within the
transmission housing, wherein the second planetary gear set is
adjacent the first wall, the first planetary gear set is adjacent
the second planetary gear set, the third planetary gear set is
adjacent the second wall, and the fourth planetary gear set is
between the first and third planetary gear sets, each planetary
gear set having a sun gear member, a ring gear member, and a planet
carrier member supporting a plurality of planet gears each
configured to intermesh with both the sun gear member and the ring
gear member, wherein the input member is continuously
interconnected with the planet carrier member of the second
planetary gear set, and the output member is continuously
interconnected with the planet carrier member of the fourth
planetary gear set and the planet carrier member of the third
planetary gear set, and wherein the ring gear member of the fourth
planetary gear set is permanently coupled to the planet carrier
member of the first planetary gear set; wherein the transmission
housing has a first area defined radially inward from an outer
periphery of the planetary gear sets and axially bounded by the
first wall and the second planetary gear set, a second area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the second and first planetary gear sets, a
third area defined radially inward from the outer periphery of the
planetary gear sets and axially bounded by the first and fourth
planetary gear sets, a fourth area defined radially inward from the
outer periphery of the planetary gear sets and axially bounded by
the fourth and third planetary gear sets, a fifth area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the third planetary gear set and the second
wall, and a sixth area defined radially inward from the third wall
and radially outward from the outer periphery of the planetary gear
sets and axially bounded by the first wall and the second wall; a
first clutch selectively engageable to interconnect the sun gear
member of the fourth planetary gear set to the planet carrier
member of the second planetary gear set; a second clutch
selectively engageable to interconnect the sun gear member of the
fourth planetary gear set to the sun gear member of the third
planetary gear set and the ring gear member of the second planetary
gear set; a third clutch selectively engageable to interconnect the
sun gear member of the fourth planetary gear set to the ring gear
member of the third planetary gear set; a first brake selectively
engageable to interconnect the sun gear member of the first
planetary gear set and the sun gear member of the second planetary
gear set to the transmission housing; and a second brake
selectively engageable to interconnect the ring gear member of the
first planetary gear set to the transmission housing, wherein the
first clutch is located in at least one of the first, second,
third, and sixth areas, the second clutch is located in at least
one of the first, second, third, and sixth areas, the third clutch
is located in at least one of the fourth, fifth, and sixth areas,
the first brake is located in at least one of the first, second,
fifth, and sixth areas, and the second brake is located in at least
one of the first, second, fifth, and sixth areas, and wherein the
clutches and brakes are selectively engageable to establish at
least eight forward speed ratios and at least one reverse speed
ratio between the input member and the output member.
2. The transmission of claim 1 wherein the first clutch is located
in the first area, the second clutch is located in the first area,
the third clutch is located in the fourth area, the first brake is
located in the sixth area, and the second brake is located in the
sixth area.
3. The transmission of claim 1 wherein each of the first, second,
third, fourth, and fifth areas are bounded axially by the outer
peripheries of the first and second walls and the outer peripheries
of the first, second, third, and fourth planetary gear sets.
4. The transmission of claim 1 wherein the first clutch is located
in the first area.
5. The transmission of claim 1 wherein the first clutch is located
in the second area.
6. The transmission of claim 1 wherein the first clutch is located
in the third area.
7. The transmission of claim 1 wherein the first clutch is located
in the sixth area.
8. The transmission of claim 1 wherein the second clutch is located
in the first area.
9. The transmission of claim 1 wherein the second clutch is located
in the second area.
10. The transmission of claim 1 wherein the second clutch is
located in the third area.
11. The transmission of claim 1 wherein the second clutch is
located in the sixth area.
12. The transmission of claim 1 wherein the third clutch is located
in the fourth area.
13. The transmission of claim 1 wherein the third clutch is located
in the fifth area.
14. The transmission of claim 1 wherein the third clutch is located
in the sixth area.
15. The transmission of claim 1 wherein the first brake is located
in the first area.
16. The transmission of claim 1 wherein the first brake is located
in the second area.
17. The transmission of claim 1 wherein the first brake is located
in the fifth area.
18. The transmission of claim 1 wherein the first brake is located
in the sixth area.
19. The transmission of claim 1 wherein the second brake is located
in the first area.
20. The transmission of claim 1 wherein the second brake is located
in the second area.
21. The transmission of claim 1 wherein the second brake is located
in the fifth area.
22. The transmission of claim 1 wherein the second brake is located
in the sixth area.
23. A transmission comprising: an input member; an output member; a
transmission housing having a first wall, a second wall, and a
third wall extending between the first and second walls; a first,
second, third and fourth planetary gear set disposed within the
transmission housing, wherein the second planetary gear set is
adjacent the first wall, the first planetary gear set is adjacent
the second planetary gear set, the third planetary gear set is
adjacent the second wall, and the fourth planetary gear set is
between the first and third planetary gear sets, each planetary
gear set having a sun gear member, a ring gear member, and a planet
carrier member supporting a plurality of planet gears each
configured to intermesh with both the sun gear member and the ring
gear member, wherein the input member is continuously
interconnected with the planet carrier member of the second
planetary gear set, and the output member is continuously
interconnected with the planet carrier member of the fourth
planetary gear set and the planet carrier member of the third
planetary gear set, and wherein the ring gear member of the fourth
planetary gear set is permanently coupled to the planet carrier
member of the first planetary gear set; wherein the transmission
housing has a first area defined radially inward from an outer
periphery of the planetary gear sets and axially bounded by the
first wall and the second planetary gear set, a second area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the second and first planetary gear sets, a
third area defined radially inward from the outer periphery of the
planetary gear sets and axially bounded by the first and fourth
planetary gear sets, a fourth area defined radially inward from the
outer periphery of the planetary gear sets and axially bounded by
the fourth and third planetary gear sets, a fifth area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the third planetary gear set and the second
wall, and a sixth area defined radially inward from the third wall
and radially outward from the outer periphery of the planetary gear
sets and axially bounded by the first wall and the second wall; a
first clutch selectively engageable to interconnect the sun gear
member of the fourth planetary gear set to the planet carrier
member of the second planetary gear set; a second clutch
selectively engageable to interconnect the sun gear member of the
fourth planetary gear set to the sun gear member of the third
planetary gear set and the ring gear member of the second planetary
gear set; a third clutch selectively engageable to interconnect the
sun gear member of the fourth planetary gear set to the ring gear
member of the third planetary gear set; a first brake selectively
engageable to interconnect the sun gear member of the first
planetary gear set and the sun gear member of the second planetary
gear set to the transmission housing; and a second brake
selectively engageable to interconnect the ring gear member of the
first planetary gear set to the transmission housing, wherein the
first clutch is located in at least one of the first, second,
third, and sixth areas when the second clutch is located in the
first area, the third clutch is located in the fourth area, the
first brake is located in the sixth area, and the second brake is
located in the sixth area, wherein the second clutch is located in
at least one of the first, second, third, and sixth areas when the
first clutch is located in the first area, the third clutch is
located in the fourth area, the first brake is located in the sixth
area, and the second brake is located in the sixth area, wherein
the third clutch is located in at least one of the fourth, fifth,
and sixth areas when the first clutch is located in the first area,
the second clutch is located in the first area, the first brake is
located in the sixth area, and the second brake is located in the
sixth area, wherein the first brake is located in at least one of
the first, second, fifth, and sixth areas when the first clutch is
located in the first area, the second clutch is located in the
first area, the third clutch is located in the fourth area, and the
second brake is located in the sixth area, wherein the second brake
is located in at least one of the first, second, fifth, and sixth
areas when the first clutch is located in the first area, the
second clutch is located in the first area, the third clutch is
located in the fourth area, and the first brake is located in the
sixth area, and wherein the clutches and brakes are selectively
engageable to establish at least eight forward speed ratios and at
least one reverse speed ratio between the input member and the
output member.
24. The transmission of claim 23 wherein each of the first, second,
third, fourth, and fifth areas are bounded axially by the outer
peripheries of the first and second walls and the outer peripheries
of the first, second, third, and fourth planetary gear sets.
25. A transmission comprising: an input member; an output member; a
transmission housing having a first wall, a second wall, and a
third wall extending between the first and second walls; a first,
second, third and fourth planetary gear set disposed within the
transmission housing, wherein the second planetary gear set is
adjacent the first wall, the first planetary gear set is adjacent
the second planetary gear set, the third planetary gear set is
adjacent the second wall, and the fourth planetary gear set is
between the first and third planetary gear sets, each planetary
gear set having a sun gear member, a ring gear member, and a planet
carrier member supporting a plurality of planet gears each
configured to intermesh with both the sun gear member and the ring
gear member, wherein the input member is continuously
interconnected with the planet carrier member of the second
planetary gear set, and the output member is continuously
interconnected with the planet carrier member of the fourth
planetary gear set and the planet carrier member of the third
planetary gear set, and wherein the ring gear member of the fourth
planetary gear set is permanently coupled to the planet carrier
member of the first planetary gear set; wherein the transmission
housing has a first area defined radially inward from an outer
periphery of the planetary gear sets and axially bounded by the
first wall and the second planetary gear set, a second area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the second and first planetary gear sets, a
third area defined radially inward from the outer periphery of the
planetary gear sets and axially bounded by the first and fourth
planetary gear sets, a fourth area defined radially inward from the
outer periphery of the planetary gear sets and axially bounded by
the fourth and third planetary gear sets, a fifth area defined
radially inward from the outer periphery of the planetary gear sets
and axially bounded by the third planetary gear set and the second
wall, and a sixth area defined radially inward from the third wall
and radially outward from the outer periphery of the planetary gear
sets and axially bounded by the first wall and the second wall; a
first clutch selectively engageable to interconnect the sun gear
member of the fourth planetary gear set to the planet carrier
member of the second planetary gear set; a second clutch
selectively engageable to interconnect the sun gear member of the
fourth planetary gear set to the sun gear member of the third
planetary gear set and the ring gear member of the second planetary
gear set; a third clutch selectively engageable to interconnect the
sun gear member of the fourth planetary gear set to the ring gear
member of the third planetary gear set; a first brake selectively
engageable to interconnect the sun gear member of the first
planetary gear set and the sun gear member of the second planetary
gear set to the transmission housing; and a second brake
selectively engageable to interconnect the ring gear member of the
first planetary gear set to the transmission housing, wherein the
first clutch is located in the first area, the second clutch is
located in the first area, the third clutch is located in the
fourth area, the first brake is located in the sixth area, and the
second brake is located in the sixth area, and wherein the clutches
and brakes are selectively engageable to establish at least eight
forward speed ratios and at least one reverse speed ratio between
the input member and the output member.
Description
FIELD
The invention relates generally to a multiple speed transmission
having a plurality of planetary gear sets and a plurality of torque
transmitting devices and more particularly to a transmission having
eight or more speeds, four planetary gear sets and a plurality of
torque transmitting devices.
BACKGROUND
The statements in this section merely provide background
information related to the present disclosure and may or may not
constitute prior art.
A typical multiple speed transmission uses a combination of a
plurality of torque transmitting mechanisms, planetary gear
arrangements and fixed interconnections to achieve a plurality of
gear ratios. The number and physical arrangement of the planetary
gear sets, generally, are dictated by packaging, cost and desired
speed ratios.
While current transmissions achieve their intended purpose, the
need for new and improved transmission configurations which exhibit
improved performance, especially from the standpoints of
efficiency, responsiveness and smoothness and improved packaging,
primarily reduced size and weight, is essentially constant.
Accordingly, there is a need for an improved, cost-effective,
compact multiple speed transmission.
SUMMARY
A transmission is provided having an input member, an output
member, a plurality of planetary gear sets, and a plurality of
torque-transmitting mechanisms. The plurality of planetary gear
sets each have a sun gear member, a planetary carrier member, and a
ring gear member.
In one aspect of the present invention, four of the gear sets are
simple planetary gear sets.
In another aspect of the present invention, two of the plurality of
torque transmitting mechanisms are brakes.
In another aspect of the present invention, three of the torque
transmitting mechanisms are friction clutches.
Further areas of applicability will become apparent from the
description provided herein. It should be understood that the
description and specific examples are intended for purposes of
illustration only and are not intended to limit the scope of the
present disclosure.
DRAWINGS
The drawings described herein are for illustration purposes only
and are not intended to limit the scope of the present disclosure
in any way.
FIG. 1A is a schematic diagram of a transmission according to the
principles of the present invention;
FIG. 1B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 1A;
FIG. 1C is a schematic diagram of another arrangement of the
transmission according to the principles of the present
invention;
FIG. 1D is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 1C;
FIG. 2A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present
invention;
FIG. 2B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 2A;
FIG. 3A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present
invention;
FIG. 3B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 3A;
FIG. 4A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present
invention;
FIG. 4B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 4A;
FIG. 5A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present
invention;
FIG. 5B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 5A;
FIG. 6A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present
invention;
FIG. 6B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 6A;
FIG. 7A is a schematic diagram of still another arrangement of the
transmission according to the principles of the present invention;
and
FIG. 7B is a chart showing feasible locations of the torque
transmitting devices for the arrangement of the transmission shown
in FIG. 7A.
DETAILED DESCRIPTION
The following description is merely exemplary in nature and is not
intended to limit the present disclosure, application, or uses.
Referring now to FIG. 1A, an embodiment of a multi-speed or eight
speed transmission is generally indicated by reference number 10.
The transmission 10 is illustrated as a rear-wheel drive or
longitudinal transmission, though various other types of
transmission configurations may be employed. The transmission 10
includes a transmission housing 11, an input shaft or member 12,
and an output shaft or member 14. The input member 12 is
continuously connected to an engine (not shown) or to a turbine of
a torque converter (not shown). The output member 14 is
continuously connected with a final drive unit (not shown) or
transfer case (not shown).
The transmission 10 includes a first planetary gear set 16, a
second planetary gear set 18, a third planetary gear set 20, and a
fourth planetary gear set 22. The planetary gear sets 16, 18, 20
and 22 are connected between the input member 12 and the output
member 14. In a preferred embodiment of the present invention, the
planetary gear set 16 includes a sun gear member 24, a ring gear
member 26, and a planet carrier member 28 that rotatably supports a
set of planet or pinion gears 30 (only one of which is shown). The
pinion gears 30 are configured to intermesh with the sun gear
member 24 and the ring gear member 26. The sun gear member 24 is
connected for common rotation with a first shaft or intermediate
member 32 and a second shaft or intermediate member 34. It should
be appreciated that the first intermediate member 32 is connected
for common rotation with the second intermediate member 34 and that
the intermediate members 32 and 34 may form one single shaft or
multiple shafts through one or more members of the planetary gear
sets, as seen throughout the several views. The ring gear member 26
is connected for common rotation with a third shaft or intermediate
member 36. The planet carrier member 28 is connected for common
rotation with a fourth shaft or intermediate member 38.
The planetary gear set 18 includes a sun gear member 42, a ring
gear member 44, and a planet carrier member 46 that rotatably
supports a set of planet or pinion gears 48. The pinion gears 48
are configured to intermesh with the sun gear member 42 and the
ring gear member 44. The sun gear member 42 is connected for common
rotation with the second intermediate member 34. The ring gear
member 44 is connected for common rotation with a fifth shaft or
intermediate member 50. The planet carrier member 46 is connected
for common rotation with the input member 12.
The planetary gear set 20 includes a sun gear member 52, a ring
gear member 54, and a carrier member 56 that rotatably supports a
set of planet or pinion gears 58. The pinion gears 58 are
configured to intermesh with the sun gear member 52 and the ring
gear member 54. The sun gear member 52 is connected for common
rotation with the fifth shaft or intermediate member 50 and with a
sixth shaft or intermediate member 51. It should be appreciated
that the fifth intermediate member 50 is connected for common
rotation with the sixth intermediate member 51 and that the
intermediate members 50 and 51 may form one single shaft or
multiple shafts through one or more members of the planetary gear
sets, as seen throughout the several views. The ring gear member 54
is connected for common rotation with a seventh shaft or
intermediate member 60. The planet carrier member 56 is connected
for common rotation with an eighth shaft or intermediate member 62.
It should be appreciated that the eighth intermediate member 62 is
connected for common rotation with the output member 14 and that
the eighth intermediate members 62 and the output member 14 may
form one single shaft or multiple shafts through one or more
members of the planetary gear sets, as seen throughout the several
views.
The planetary gear set 22 includes a sun gear member 72, a ring
gear member 74, and a planet carrier member 76 that rotatably
supports a set of planet or pinion gears 78. The pinion gears 78
are configured to intermesh with the sun gear member 72 and the
ring gear member 74. The sun gear member 72 is connected for common
rotation with a ninth shaft or intermediate member 64 and a tenth
shaft or intermediate member 66. It should be appreciated that the
ninth intermediate member 64 is connected for common rotation with
the tenth intermediate member 66 and that the intermediate members
64 and 66 may form one single shaft or multiple shafts through one
or more members of the planetary gear sets, as seen throughout the
several views. The ring gear member 74 is connected for common
rotation with the fourth intermediate member 38. The planet carrier
member 76 is connected for common rotation with the output member
14 and with the eighth intermediate member 62.
The transmission 10 includes a variety of torque-transmitting
mechanisms or devices including a first intermediate clutch C1, a
second intermediate clutch C2, a third intermediate clutch C3, a
first brake B1 and a second brake B2. The first intermediate clutch
C1 is selectively engagable to connect the input member 12 to the
tenth intermediate member 66. Alternatively, the first intermediate
clutch C1 may be connected to the input member 12 through the
planet carrier member 46, as seen throughout the several views. The
second intermediate clutch C2 is selectively engagable to connect
the sixth intermediate member 51 to the ninth intermediate member
64. The third intermediate clutch C3 is selectively engagable to
connect the seventh intermediate member 60 to the ninth
intermediate member 64. The brake B1 is selectively engagable to
connect the first intermediate member 32 to the transmission
housing 11 to restrict rotation of the first intermediate member 32
relative to the transmission housing 11. Finally, the brake B2 is
selectively engagable to connect the third intermediate member 36
to the transmission housing 11 to restrict rotation of the third
intermediate member 36 relative to the transmission housing 11.
The transmission 10 is capable of transmitting torque from the
input member 12 to the output member 14 in at least eight forward
torque ratios and one reverse torque ratio. Each of the forward
torque ratios and the reverse torque ratio are attained by
engagement of one or more of the torque-transmitting mechanisms
(i.e. first intermediate clutch C1, second intermediate clutch C2,
third intermediate clutch C3, brake B1 and brake B2). Those skilled
in the art will readily understand that a different speed ratio is
associated with each torque ratio. Thus, eight forward speed ratios
may be attained by the transmission 10.
The transmission housing 11 includes a first end wall 102, a second
end wall 104, and a third wall 106. The third wall 106
interconnects between the first and second end walls 102 and 104 to
provide a space or cavity 108 in which planetary gear sets 16, 18,
20, and 22 and the torque-transmitting mechanisms C1, C2, C3, B1,
and B2 are located. Further, the cavity 108 has a plurality of
areas or Zones A, B, C, D, E, and F in which the plurality of
torque transmitting mechanisms C1, C2, C3, B1, and B2 will be
specifically positioned, in accordance with the preferred
embodiments of the present invention.
As shown in FIG. 1A and throughout the several views, Zone A is
defined by the area or space bounded: axially on the left by the
first end wall 102, on the right by planetary gear set 16, radially
inward by a reference line "L" which is a longitudinal line that is
axially aligned with the input shaft 12, and radially outward by a
reference line "M" which is a longitudinal line that extends
adjacent an outer diameter or outer periphery of the planetary gear
sets 16, 18, 20, and 22. While reference line "M" is illustrated as
a straight line throughout the several views, it should be
appreciated that reference line "M" follows the outer periphery of
the planetary gear sets 16, 18, 20, and 22, and accordingly may be
stepped or non-linear depending on the location of the outer
periphery of each of the planetary gear sets 16, 18, 20, and 22.
Zone B is defined by the area bounded: axially on the left by
planetary gear set 16, axially on the right by the planetary gear
set 18, radially outward by reference line "M", and radially inward
by reference line "L". Zone C is defined by the area bounded:
axially on the left by the planetary gear set 18, axially on the
right by the planetary gear set 20, radially outward by reference
line "M", and radially inward by reference line "L". Zone D is
defined by the area bounded: axially on the left by the planetary
gear set 20, axially on the right by the planetary gear set 22,
radially outward by reference line "M", and radially inward by
reference line "L". Zone E is defined by the area bounded: axially
on the left by the planetary gear set 22, axially on the right by
the second end wall 104, radially outward by reference line "M",
and radially inward by reference line "L". Zone F is defined by the
area bounded: axially on the left by the first end wall 102,
axially on the right by the second end wall 104, radially inward by
reference line "M" and radially outward by the third wall 106. As
will be described and illustrated hereinafter, planetary gear sets
16, 18, 20, and 22 will change positions within the transmission
cavity 108, however, the Zones described above will not change and
will remain the same as shown throughout the Figures.
In the arrangement of the transmission 10 shown in FIG. 1A, the
planetary gear sets 16, 18, 20, and 22 are longitudinally arranged
in the following order from left to right: 16-18-20-22.
Specifically, the planetary gear set 16 is disposed closest to the
wall 102, the planetary gear set 22 is disposed closest to the wall
104, the planetary gear set 18 is adjacent the planetary gear set
16, and the planetary gear set 20 is disposed between the planetary
gear sets 18 and 22. The torque-transmitting mechanisms are
intentionally located within specific Zones in order to provide
advantages in overall transmission size, packaging efficiency, and
reduced manufacturing complexity. In the particular example shown
in FIG. 1A, the torque-transmitting mechanism C1 is disposed within
Zone C, the torque-transmitting mechanisms C2 and C3 are disposed
within Zone D, and the torque-transmitting mechanisms B1 and B2 are
disposed within Zone F.
However, the present invention contemplates other embodiments where
the torque-transmitting mechanisms C1, C2, C3, B1, and B2 are
disposed in the other Zones. The feasible locations of the
torque-transmitting devices C1, C2, C3, B1, and B2 relative to the
Zones are illustrated in the chart shown in FIG. 1B. An "X" in the
chart indicates that the present invention contemplates locating
the particular torque-transmitting device in any of the referenced
Zones.
With reference to FIG. 1C, an alternate embodiment of the
multi-speed transmission is indicated by reference number 10B. The
transmission 10B includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation.
The transmission 10B includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged identically to the arrangement shown
in FIG. 1A. However, in the particular example shown in FIG. 1C,
the torque-transmitting mechanisms C1 and C2 are disposed within
Zone B. As in the previous embodiment, the torque-transmitting
mechanism C3 is disposed within Zone D and the torque-transmitting
mechanisms B1 and B2 are disposed within Zone F.
Additionally, the present invention contemplates other embodiments
of transmission 10B where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
1D. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
Turning now to FIG. 2A, still another embodiment of the multi-speed
transmission is indicated by reference number 200. The transmission
200 includes the planetary gear sets 16, 18, 20, and 22 and the
torque-transmitting mechanisms C1, C2, C3, B1, and B2. The various
components and connecting shafts that are identical with the
transmission 10 in FIG. 1A have the same numerical designation in
FIG. 2A.
The transmission 200 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged in the following order from left to
right: 18-20-16-22. Specifically, the planetary gear set 18 is
disposed closest to the wall 102, the planetary gear set 22 is
disposed closest to the wall 104, the planetary gear set 20 is
adjacent the planetary gear set 18, and the planetary gear set 16
is disposed between the planetary gear sets 20 and 22. The
torque-transmitting mechanisms are intentionally located within
specific Zones in order to provide advantages in overall
transmission size, packaging efficiency, and reduced manufacturing
complexity. In the particular example shown in FIG. 2A, the
torque-transmitting mechanisms C1 and C2 are disposed within Zone
A, the torque-transmitting mechanism C3 is disposed within Zone C,
and the torque-transmitting mechanisms B1 and B2 are disposed
within Zone F.
However, the present invention contemplates other embodiments of
the transmission 200 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
2B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
With reference to FIG. 3A, still another embodiment of the
multi-speed transmission is indicated by reference number 300. The
transmission 300 includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation in FIG. 3A.
The transmission 300 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged identically to the arrangement shown
in FIG. 2A. However, the input shaft 12 is arranged such that it
crosses the boundary between Zones A and F. In the particular
example shown in FIG. 3A, the torque-transmitting mechanisms C1 and
C2 are disposed within Zone A, the torque-transmitting mechanism C3
is disposed within Zone C, and the torque-transmitting mechanisms
B1 and B2 are disposed within Zone F.
However, the present invention contemplates other embodiments of
the transmission 300 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
3B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
With reference to FIG. 4A, still another embodiment of the
multi-speed transmission is indicated by reference number 400. The
transmission 400 includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation in FIG. 4A.
The transmission 400 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged in the following order from left to
right: 18-16-20-22. Specifically, the planetary gear set 18 is
disposed closest to the wall 102, the planetary gear set 22 is
disposed closest to the wall 104, the planetary gear set 16 is
adjacent the planetary gear set 18, and the planetary gear set 20
is disposed between the planetary gear sets 16 and 22. The
torque-transmitting mechanisms are intentionally located within
specific Zones in order to provide advantages in overall
transmission size, packaging efficiency, and reduced manufacturing
complexity. In the particular example shown in FIG. 4A, the
torque-transmitting mechanisms C1 and C2 are disposed within Zone
A, the torque-transmitting mechanism C3 is disposed within Zone C,
and the torque-transmitting mechanisms B1 and B2 are disposed
within Zone F.
However, the present invention contemplates other embodiments of
the transmission 400 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
4B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
With reference to FIG. 5A, still another embodiment of the
multi-speed transmission is indicated by reference number 500. The
transmission 500 includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation in FIG. 5A.
The transmission 500 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged in the following order from left to
right: 18-16-22-20. Specifically, the planetary gear set 18 is
disposed closest to the wall 102, the planetary gear set 20 is
disposed closest to the wall 104, the planetary gear set 16 is
adjacent the planetary gear set 18, and the planetary gear set 22
is disposed between the planetary gear sets 16 and 20. The
torque-transmitting mechanisms are intentionally located within
specific Zones in order to provide advantages in overall
transmission size, packaging efficiency, and reduced manufacturing
complexity. In the particular example shown in FIG. 5A, the
torque-transmitting mechanisms C1 and C2 are disposed within Zone
A, the torque-transmitting mechanism C3 is disposed within Zone D,
and the torque-transmitting mechanisms B1 and B2 are disposed
within Zone F.
However, the present invention contemplates other embodiments of
the transmission 500 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
5B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
With reference to FIG. 6A, still another embodiment of the
multi-speed transmission is indicated by reference number 600. The
transmission 600 includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation in FIG. 6A.
The transmission 600 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged in the following order from left to
right: 20-18-16-22. Specifically, the planetary gear set 20 is
disposed closest to the wall 102, the planetary gear set 22 is
disposed closest to the wall 104, the planetary gear set 18 is
adjacent the planetary gear set 20, and the planetary gear set 16
is disposed between the planetary gear sets 18 and 22. The
torque-transmitting mechanisms are intentionally located within
specific Zones in order to provide advantages in overall
transmission size, packaging efficiency, and reduced manufacturing
complexity. In the particular example shown in FIG. 6A, the
torque-transmitting mechanisms C1, C2, B1, and B2 are disposed
within Zone F, and the torque-transmitting mechanism C3 is disposed
within Zone A.
However, the present invention contemplates other embodiments of
the transmission 600 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
6B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
With reference to FIG. 7A, still another embodiment of the
multi-speed transmission is indicated by reference number 700. The
transmission 700 includes the planetary gear sets 16, 18, 20, and
22 and the torque-transmitting mechanisms C1, C2, C3, B1, and B2.
The various components and connecting shafts that are identical
with the transmission 10 in FIG. 1A have the same numerical
designation in FIG. 7A.
The transmission 700 includes the planetary gear sets 16, 18, 20,
and 22 longitudinally arranged in the following order from left to
right: 20-22-18-16. Specifically, the planetary gear set 20 is
disposed closest to the wall 102, the planetary gear set 16 is
disposed closest to the wall 104, the planetary gear set 22 is
adjacent the planetary gear set 20, and the planetary gear set 18
is disposed between the planetary gear sets 22 and 16. The
torque-transmitting mechanisms are intentionally located within
specific Zones in order to provide advantages in overall
transmission size, packaging efficiency, and reduced manufacturing
complexity. In the particular example shown in FIG. 7A, the
torque-transmitting mechanisms C1, C2, and C3 are disposed within
Zone B, the torque-transmitting mechanism B1 is disposed within
Zone F, and the torque-transmitting mechanism B2 is disposed within
Zone E.
However, the present invention contemplates other embodiments of
the transmission 700 where the torque-transmitting mechanisms C1,
C2, C3, B1, and B2 are disposed in the other Zones. The feasible
locations of the torque-transmitting devices C1, C2, C3, B1, and B2
relative to the Zones are illustrated in the chart shown in FIG.
7B. An "X" in the chart indicates that the present invention
contemplates locating the particular torque-transmitting device in
any of the referenced Zones.
The description of the invention is merely exemplary in nature and
variations that do not depart from the gist of the invention are
intended to be within the scope of the invention. Such variations
are not to be regarded as a departure from the spirit and scope of
the invention.
* * * * *